Paper cutting machine



1938. F. w. sEYBoLb 2,127,432

PAPER CUTTING MACHINE Filed Nov. 7, 1936 10 Sheets-Sheet l Aug. 16, 1938. F. WfSEY BOLD ,4

PAPER CUTTING MACHINE Filed Nov. 7, 1936 1o Sheets-Sheet 2 1938. F. w. SEYBOLD Y 2,127,432

PAPER CUTTING MACHINE Filed Nov. 7, 1936 10 Sheets-Sheet 3 8- 6, 1933. 1 F. w. sEYBo b 2,127,432

PAPER CUTTING MACHINE Filed Nov. '7, 1956 I 10 Sheets-Sheet 4 IIIH Aug. 16, 1938. F. w. SEYBOLD ,1

I PAPER CUTTING MACHINE I Fild Nov. 7, 1936 10 sheets-sheets II I Aug. 16, 1938. F. w. SEY BOLD PAPER CUTTING MACHINE Filed Nov. Z, 1936 1o Shee ts-Sheet a Aug/16, 1938. F. w. sEYBbLD PAPER CUTTING MACHINE Filed Nov. 7, 1936 .10 Sheets-Sheet 7 1938- I F. W. SEYBOLD 2,127,432

PAPER CUTTING MACHINE Filed Nov. '7, 1956 10 Sheets-Sheet 8 u ll m A g- 1938. F. w. SEYBOILD 2,127,432

PAPER CUTTING MACHINE Filed NOV. 7, 1936 I 10 Sheets-Sheet 9 Aug. 16, 1 938. F. w. SEYBOLD ,1 2

PAPER CUTTING MACHINE Filed Nov. 7, 1936 10 sheets-sheet 1o Patented Aug. 16, 1938 UNlTED STATES PATENT, OFFlCE to American Type Founders Incorporated,

Elizabeth, N. J., a corporation of New Jersey Application November '7, 1936, Serial No. 109,795

46 Claims.

This invention relates to cutting machines and more particularly to paper cutting and trimming machines of the type employing a knife which is adapted to reciprocate or oscillate in a vertical plane.

The general object of the invention is to provide a. novel and improved cutting machine of this character which is of a sturdy construction, powerful yet accurate in operation, and capable of a greater degree of control, in the interests of both efficiency and safety, than similar devices heretofore proposed.

Paper cutting devices of this general type are rugged and powerful motor driven machines, the larger ones being designed to cut or trim piles of paper one hundred or more inches Wide and of thicknesses up to four or five inches. However, despite the weight and sturdiness of the knife and operating mechanism, it is important that the starting and stopping of the device be effected quickly and adapted for both manual and automatic control. There must also be provided means for automatically clamping the paper firmly during the cutting operation so that there shall be no shifting nor warping of the pile.

, Furthermore, from the very nature of the device it is obvious that, in the absence of the provision of certain safety features, serious accidents might occur. These safety and protective devices should accomplish the purpose of preventing injury to the operator, to the stock, and to the machine and its driving and transmission mecha ing mechanism, if unusual resistance is encountered.

A further object of the invention is the provision of an automatic paper clamping mechanism which is adapted through the actuation of the cutter driving means to firmly clamp the pile of paper with the required pressure, which even in machines of moderate size may amount to several tons. The pressure of the clamping mechanism,

prevent undue strain or breakage of the driv furthermore, is automatically adjusted to the height of the pile of paper. Provision is also made for absorbing the preloading strain of the clamping mechanism so that the driving mechanism is relieved of the torque which might otherwise prove a source of danger to the operator.

Other objects and features of novelty will be apparent from the following specification when read in connection with the accompanying drawings in which one embodiment of the invention is illustrated by way of example.

In the drawings:

Figure 1 is a view in front elevation of a paper cutter embodying the principles of the invention;

Figure 2 is a fragmentary view in horizontal section on an enlarged scale showing a detail of the knife leveling support and taken substantially on line 2 2 of Figure 1;

Figure 3 is a fragmentary vertical sectional view taken on line 3-3 of Figure 2;

Figure 4 is a view of the cutter in rear elevation;

Figure 5 is a fragmentary view in rear elevation on an enlarged scale of certain details of mechanism shown in the lower portion of Figure Figure 6 is a vertical transverse sectional view taken just inside of the front wall of the machine or substantially on line 6--6 of Figure '7;

Figure 7 is a horizontal sectional view taken substantially on line 1-1 of Figure 6;

Figure 81s a vertical longitudinal sectional View 7 taken substantially on line 8-8 of Figure 6;

Figure 9 is a vertical longitudinal sectional view of the lower portion of the machine taken on line 9-9 of Figure 6;

Figure 10 is a fragmentary view in perspective on an enlarged scale of certain cranks and levers included in the safety mechanism controlling the Figure 13 is a view in horizontal section on a further enlarged scale of certain details of the safety driving mechanism;

Figure 14 is a view in vertical section of the i clutch actuating levers, and taken substantially .on line l4l4 of Figure 13;

Figure 15 is a view in vertical section through the gear box which is secured to the rear of the frame of the cutter;

Figures 16, 17, 18, 19, and 20 are somewhat diagrammatic views in vertical section showing various positions of operation of the non-repeating safety mechanism;

Figure 21 is a view in vertical transverse section through the lower portion of the frame of the cutter showing the automatic clamping mechanism and taken substantially on line 2I2l of Figure 7;

Figure 22 is a view in substantially vertical section taken on line 2222 of Figure 21 and illustrating a detail of the clamp operating mechanism;

Figure 23 is a substantially horizontal sectional view taken on line 23-23 of Figure 21;

Figure 24 is a substantially vertical sectional view taken on line 2424 of Figure 21; and

Figures 25 and 26 are views similar to Figure 21 illustrating two successive stages in the actuation of the clamping mechanism.

Referring now more especially to the general views comprising Figures 1, 4, 6, and 8, it will be seen that the cutting machine comprises a main frame in which preferably is formed integrally by a single casting operation. This mode of construction ensures a greater degree of strength and rigidity than a frame fabricated of several assembled parts. The main frame In in the preferred embodiment is hollow so as to provide an enclosure for part of the operating mechanism and is provided with the front wall II, the rear wall I2, and the side walls l3. The front wall I I may be slightly depressed or inset centrally of the machine as shown, the side portions of the frame being extended upwardly beyond the central portion of the front wall II to provide an arched construction indicated at [5 over the central opening across which the knife 18 is adapted to swing and through which extends the table l6 upon which the paper to be cut is placed. This table is also arranged to carry certain gauging mechanism which will be described later and is also provided with a groove adapted to receive the wooden cutting stick I! positioned immediately beneath the knife edge.

The knife The vertically oscillating knife member designated generally by the reference numeral 18 comprises the heavy knife bar or carrier [9 and the knife blade 20 which is secured to the carrier as by means of the bolts 2|. The knife I8 is guided at each side of the main frame l0 between the rearwardly facing surfaces 23 on the arch portion iii of the main frame and the rearwardly disposed guide plates 24 which are secured to the main frame ID. The knife bar I9 is bifurcated or-deeply slotted to receive the depending ends of the supporting links 25 and 2B, the pins 21 being provided to pivotally connect the bar with the lower ends of the links. The link 26 is suspended from the pin 28 and the. link 25 is suspended from the eccentric portion 29 of the pin 35 as most clearly shown in Figures 1, 2, and 3. A bushing 3! may be interposed between the link 25 and the eccentric portion of the pin 30, the main portion of the pin 30 being received in the bearing 32 provided in the upper arched portion l5 of the frame. Upon the forwardly projecting end 33 of the pin 30 there is secured a member 35 having a handle 36 and a semi-circular portion 31 provided with an arcuate slot 38 through which the screw 39 is adapted to pass. The screw 39 is threaded into the frame as'at 40 and serves to clamp the member 35 rigidly in an adjusted angular position which determines the position of the eccentric pivot portion 29 of the pin 30 which supports the link 25 of the knife. By suitable adjustment of the member 35 by means of the handle 35 the knife may be leveled so that it will strike the Wooden cutting stick I"! evenly. When the proper setting is made, the screw 33 is tightened in order to clamp the member 35 securely in the adjusted position against the face of the frame.

The right hand end 42 of the knife bar l9 as seen in Figures 1 and 6 is also bifurcated to receive the yoke 43 comprising the upper end of the pull rod 45 which is adapted to operate the knife. The intermediate portion of the pull rod i5 comprises the hexagonal turnbuckle section 45 which is provided with threads of opposite hand at each end for adjustable connection with the yoke 43 and with the eccentric strap 41 provided at the lower end of the rod. Once the desired length of the pull rod 45 is attained by rotation of the central portion 46, the adjustment may be locked by means of the nuts 48. The eccentric strap ll is carried by the eccentric member 55 which is carried by the shaft 5! which extends longitudinally, of the frame It! and is rotatably mounted in the anti-friction bearing assembiies 52, 52a and 53, the last named one being disposed in the gear casing or housing 54 fastened to the lower part of the rear wall I2 of the main frame. The driving means for this shaft 55 will be described in detail hereinafter.

The gauging mechanism In order to position the paper accurately upon the table it so that it may be cut to the proper ize and to ensure that the edges are squared up perfectly, an adjustable back gauge 55 is provided. against the vertical fingers 55' of which the rear edge of the pile is placed. The back gauge is generally made in three sections so that the parts may be arranged in staggered relation in order to facilitate the cutting and trimming of certain classes of work such as tablets and other gang work. The three sections are provided with rearwardly directed flanges 55 which are slotted as at 51 for the reception of the thumb screw clamping bolts 58, by which they are secured together.

The table !6 is provided with a central longitudinally extending slot 63, and upon its underside with a tongue Bl lying adjacent the slot 60. A slotted guide member 53, provided with a gib M, is slidably fitted upon the tongue 6|. The

central section of the back gauge 55 is securely fastened to the guide member 63 by means of the taper pin 55. At the extreme rear end of the table l6 there is provided a bracket 61 adapted to rotatably support the vertically extending post 58, upon the lower end of which is secured a sprocket wheel 69 about which the chain 70 is passed. Beneath the forward end of the table it, the hand wheel 72 is mounted to turn upon the pin 13. A sprocket wheel 14 is carried by the hand wheel 12 and the chain 10 is adapted to pass around this sprocket wheel also. Both ends of the chain ID are secured to the lugs 75 on the back gauge guide member 63 as clearly indicated in Figure 8. It will thus be seen that by turning the hand wheel 12, the gauge 55, which is connected with the guide member 53 as already described, can be moved toward or away from the knife l8 by the operator. The hand wheel 72 can be clamped in adjusted position by means of the locking handle 11, thereby locking the gauge 55 in its adjusted position.

In order to indicate to the operator the precise adjustment of the back gauge 55 the following mechanism is provided. Upon the upper end of the vertical rod 68 at the rear of the table there is provided a pulley I8. A similar Wheel or pulley I9 is rotatably mounted upon the pin 80 provided at the upper middle portion of the arch frame I5 at the forward part of the machine. The center section of the back gauge 55 carries a post 6! which is secured as at 82 to one lap of the endless graduated tape 85 which passes around the pulleys I8 and 19. The forward bend of the tape passing around the pulleys I9 is visible through the opening 85 in the front face of the frame I5 and a pointer B71 is provided in order to indicate upon the tape the distance between the back gauge 55 and the edge of the knife I8.

The driving mechanism and associated controls The power for driving the crank shaft 5| for operating the cutter is provided by an electric motor Bil upon the shaft of which is secured the V-belt pulley 9|. The motor is suspended from the pivot pins 9'2 and its position may be adjusted within certain limits in order to tighten the belt, by means of the screw 93, the inner end of which is adapted to bear against a portion of the rear wall I2 of the frame III. The V-belts 95 serve to connect the motor pulley 9| with the appropriately grooved fly wheel 96, the hub 97 of which is mounted upon the two sets of ball bearings 98 carried by the shaft Hill. The ball bearing assemblies are spaced by the sleeve 99 which fits loosely in the bore of the hub 91 of the fly wheel.

The shaft I is disposed horizontally and rearwardly of the frame II] and is journalled at one end in anti-friction bearings IIlI carried by the bracket I62. A closure plate I03 and the oil seal I64 on the bracket I62 prevent leakage of oil from the bearing. The opposite end of the shaft Hill is rotatably supported by means of the bearing assembly I56 carried by the bracket III] secured to the web I69 extending from the rear wall I2 of the main frame. Oil seals I I I and I I2 carried by the bracket I I6 prevent leakage of oil from the bearing assemblies. The flanged collar I I5, whose function will be apparent as the description proceeds, is also fitted within the bore of the bracket IIEI and abuts against the inner race of the ball bearing assembly- This collar also fits over the spline or key II6 provided in the shaft I66.

A disc clutch I26 is carried by the shaft I00 adjacent the fly wheel 56, and its driving plate I2I is operatively connected through a series of equally spaced pins I22 with the fly wheel. The jaws It'll which cause theblades of the clutch to engage are brought together by means of the sliding collar I25 which actuates the toggles I26. The actuating collar I25 is splined to the shaft I50 and is provided with an annular flange I35 which is rotatably received by the grooved split ring I3I which is provided with the trunnions I32. The clutch I25 is actuated by certain starting mechanism which is connected with the trunnions I32, and which constitutes the means for normally connecting and disconnecting the knife actuating eccentric B and the other operative mechanism with the source of power.

Another drive shaft I 55 is disposed in alignment with the shaft I00 and enters the gear case or housing 5 5, being rotatably received by the anti-friction bearing assemblies I53 having suitable lubricant retaining means applied thereto. The portion of the shaft I55 which occupies the gear box 55 is provided with a worm I55 which meshes with the worm wheel I56 carried by the shaft 5| which also carries the eccentric 56.

The left hand end of the worm shaft I50, as viewed in Figures 11, 1'2, and 13 of the drawings, has a combined brake wheel and coupling member I55 keyed thereon as at I66. This member IE5 is provided with a V-groove I61 formed peripherally therein and adapted to receive the upper and lower brake shoe elements I68 and I69 respectively. These members. are fulcrumed upon the pin I'll) which is carried by a hanger III forming an extension of the supporting bracket IE6 to which reference has already been made. Keyed upon the right hand end of the drive shaft IIIIi as at I'M is the driving coupling member I75, best shown in Figures 11, 12, and 13. The member H5 is normally urged outwardly toward the member I65 carried by the shaft I5Il by means of the springs. I'I'I which are disposed within the pockets I'IB formed in the member I75, and which bear at their outer ends against the collar II5. At diametrically oppositely disposed points in the brake wheel I65 there are inserted the hardened steel chucks I8I. At corresponding points in the member I75 there are also inserted similarly formed chuck members I82. Received Within the adjacent open ends of the chucks I8I and I62 of each pair are the small breakpins I83 which are adapted to be sheared in two and thus release the driving connection between the member I75 and the member I65 upon the occurrence of overload on the cutting mechanism or under circumstances to which reference will be made.

As more clearly disclosed in Figures 5 and 8 of the drawings, the brake shoes I68 and I69 are provided with bifurcated extensions or cars I85 which are perforated to receive the pins I85. Both of the pins I56 are provided with vertically disposed openings to receive the rod I88, the lower end of the rod being threaded into the opening in the lower pin I 86 and an intermediate portion of the rod passing freely through the opening in the upper pin I66. The upper end of the rod is provided with a small hand wheel I89 which provides an upper spring stop for the spring I95, the lower end of which rests upon the washer IQI. It is obvious that rotation of the rod I88 in one direction will serve to increase the compression in spring I96 and the compression may be decreased by rotation of the rod in the opposite direction, thus varying the clamping pressure of the brake shoes.

Between the ears or lugs I85 formed on the respective brake shoes there are disposed the flanged rollers I92 which may be pivotally carried by the pins I53 on the ends of the brake shoes. The brake shoes may be spread apart against the pressure of the spring 4 95 by means of the wedge plate I65 which. is provided with the two inclined surfaces I66 and which is extended as at I97 to be pivotally connected with one of the levers associated with the starting mechanism, so that the brake will be simultaneously released when the clutch I25 is engaged and vice versa. A steadying bolt I98 is secured to an extension I 95 of the bracket M6 and has a bifurcated end 266 which is extended through the slot 26! in the wedge plate I95 and embraces the rod I65 in order'to support and guide it, all as clearly shown in Figures 5 and 13.

Referring now more particularly to Figures 11 and 14 of the drawings it'will be seen that the trunnions I32 of the clutch actuating collar I25 are engaged by the forked lower ends of the levers 205 and 296 which are fulcrumed upon the pin 201 carried by an extension 208 of the bracket H0. The lever 206 has an angular offset arm 209 to which the shank I91 of the brake actuating wedge plate I95 is pivotally connected as at 2I0. The upper ends of the levers 205, 206 are connected by the transverse pivot pin 2I2 which is also received within the slightly elongated opening H3 in the lower end of the crank 2I5 which is carried by the shaft 2I6 which has the bearings 2 I I and 2 I8 in the rearward and forward walls I2 and II respectively of the main frame of the cutter, as clearly shown in Figure 8 of the drawings. Secured to the forward end 220 of the shaft 2I6, which projects exteriorly of the front wall II of the frame, is the upwardly extending crank 22I which is connected at its end by a horizontally extending link 222 with the end of the crank arm 223 carried by the longitudinally extending actuating shaft 225. Upon the forwardly projecting end-of the shaft 225 there is fixed the starting lever 226 which is provided with the handle 221 for manual actuation. It will be noted that the link 222 is provided with a pin and slot connection as at 228 with the crank 223 so that the hand lever may be raised to some extent without moving the link 222.

It will be seen that when the starting lever 226 is depressed, the shaft 225 will be rotated in a clockwise direction as viewed in Figures 1 and 11, the shaft 2I6 will be rotated in a counterclockwise direction, the connecting pin 2I2 will be moved toward the right in Figure 11, and the lower ends of the levers 205 and 206 will be moved toward the left carrying with them the clutch actuating sleeve I25 and causing the clutch I20 to engage so that power is transmitted from the fly wheel pulley 96 to the shaft 00 and thus through the break pin driving connection to the worm shaft I50 and thence through the worm wheel I56 and the longitudinal shaft 5i to the eccentric 50.

As best seen in Figures 12 and 14 of the drawings, the pin 2 I2 which serves to connect the levers 205 and 206 with the crank arm 2 I 5 also provides a pivotal connection for the lower end 233 of the rod 235 which passes near its upper end through the head of the eye bolt 236 which is rigidly secured to the frame I as at 231 (see also Figures 7 and 8). The rod 235 is adapted to pass freely through the head 236 of the eye bolt and is provided at its upper end with the head or collar 238. Seated between the shouldered lower end 233 of the rod 235 and the head 236 of the eye bolt is the coil spring 245! which serves to urge the rod 235 downwardly and actuate the levers 205 and 206 to release the clutch I20. This motion is limited, of course, by the contact of the head 238 of the rod with the eye bolt 236.

The hand crank shaft 225 extends entirely through the frame I0, being rotatably mounted in the front and rear bearings 242 and 243 pro vided in the forward and rear walls II and I2 respectively. The shaft 225 projects rearwardly of the frame and, just beyond the bearing boss 243, freely rotatably carries the sleeve 245 from which projects the crank arm 246 and from which depends the angular latch member 250 having a squared end 25I adapted to be interposed between the eye bolt 235 and the head 238 of the spring rod 235 as clearly shown in Figures 4 and 12 of the drawings. Upon the extreme rear end of the shaft 225 there is fulcrumed the lever 254, the upper arm 255 of which is parallel with and connected to the end of the crank 246 by means of the pin 256 which carries a spacing sleeve 251 disposed between the arms 246 and 255. The lower arm 266 of the lever 254 is curved outwardly and downwardly as shown in Figures 4, '1, 9, and 12 and is provided at its lower end with a roller 26I which is adapted to be contacted by the cam member 262 carried by the rearwardly projecting end of the shaft 51 which extends through the rear wall of the gear box 54'. This cam 262 is so designed with relation to the eccentric 50, carried by the same shaft as to actuate the lever 254 at the end of every cutting stroke of the knife. It will be seen that upon movement of the lever 254 under the influence of the cam, the arms 255 and 246 will be depressed and the latch member 250 will be rotated in a counter-clockwise direction as viewed in Figure 12, the spring rod 235 will be depressed, the clutch I20 will be released, and the brake I65 will be set.

Upon the hand crank shaft 225 between the sleeve 245 and the fulcrum of the lever 254, there is keyed a sleeve 210 which is provided with an arm 21I which projects above the connecting sleeve 251 which extends between the lever arms 246 and 255. The sleeve 216 is also provided with a bifurcated arm 212 which is adapted to em.- brace the safety stop rod 215. This rod 215 is provided with a head 216 and a flange 211 both providing seats for the springs 218 and 219 which cause the upper and lower washers 280 to bear against the curved surfaces of the bifurcated arm 212 at all times. There is thus provided a resilient lost motion operating connection between the arm 212 and the safety rod 215. The lower end portion of the rod 215 passes through the bearings 282 and enters the gear case 54 where it is adapted for blocking engagement with the driving mechanism under certain conditions which will be hereinafter described.

Depending from a pivotal connection with the pin 256 adjacent the end of the arm 246 is the substantially vertically disposed link 285 which,

as shown best in Figure 12, is pivotally connected at its lower end with the arm 286 of a bell crank lever 281 fulcrumed on the-pin 288 secured to the frame I0. The opposite arm 289 of the bell crank lever is provided with a roller 290 which is adapted to be contacted by the flange 292 of the driving member I15 when the break pins I83 are sheared off under conditions of excessive load or upon actuation of the emergency stop which will be described. In order to effect this contact upon breakage of the pins the following mechanism is provided. In Figure 13 of the drawings it will be seen that pins 295 are received in the brake wheel I65 at diametrically opposite points which may be equally spaced from the position of the chucks I8I. The pins 295 are provided with conical heads 296 which normally enter similarly shaped depressions 291 in the drive member I15. It will thus be seen that upon the severing of the break pins I83, the conical heads 296 will force the member I15 to the left upon continued rotation thereof after stoppage of the brake member I65. This will cause the bell crank lever 281 to rock in a clockwise direction as viewed in Figure 12, which will, through the link 285, move the arm 245 downwardly and withdraw the latch member 250 from beneath the head 238 of the spring rod 235, thus effecting the release of the clutch I20 as has already been explained.

It will now be seen that there are three ways in which the latch member 250 will be rotated in order to release the spring rod 235 and open the clutch. First, this may be effected by a reverse or counterclockwise rotation of the hand crank 226. This will cause a similar rotation of the shaft 225 and the sleeve 21!) which will cause the arm 21I to contact with the connecting sleeve 251 and rock the arm 206 downwardly, thus removing the latch 250 with which said arm is integrally connected. Secondly, the latch member 250 will normally be automatically released at the end of each cutting stroke by means of the cam 252 acting through the lever 254 which through its upper arm 255 is connected with the latch crank 246, 250. Also, the latch 250 will be removed as has been described, by breakage of the pins I83 which will cause the drive member I15 to move to the left and rotate the latchcrank members through the bell crank 281 and the link 205. It should be pointed out that due to the configuration of the member 245, 246, 250 and the relation of the other parts thereto, the latch 250 will engage beneath the head 238 of the spring rod 235 by gravity, when it is not acted upon by any of the forces which have just been described. Engagement of the clutch 120 is therefore always maintained by means of the latch until the latter is positively removed, whereupon the pressure of the spring 240 will cause the rod 235 to descend, disengage the clutch, and through the wedge plate I95 set the brake I65.

The non-repeat safety mechanism The lower end of the safety rod 215 which projects into the casing 54 is disposed adjacent the Worm wheel I56, as clearly shown in Figures 15-19 of the drawings and is recessed as at 350 to permit the passage, under certain conditions, of the pin 30I which is carried by and projects laterally from the worm wheel. The lower side of the recess 300 is preferably of arcuate configuration as shown at 302.

Also secured to the same side of the worm wheel I56 and adapted to follow the pin 301, is the wedge member 305. During the clockwise rotation of the wheel as viewed in Figures 16-19, the wedge 305 is adapted to enter the notch or opening 300 in the safety rod 215 and, bearing against the curved surface 302, draw the rod 215 inwardly after the pin 30I has passed through the opening 300 during the first part of the cycle of rotation of the crank shaft Figure 18 shows this inward wedging movement of the rod being effected. A pivoted latch member 306 is carried by the lever arm 212 and is provided with a shoulder as at 301 which engages behind the shoulder 211 on the rod 215 when the wedge 305 has drawn the rod downwardly a suflicient distance. This ensures that the rod is retained in this depressed position during the cycle of operation of the cutter. When the rod 215 is in this depressed position the pin 30I upon again approaching the rod 215 will not register with the opening 320 (see Figure 19) but will abut the rod at a point above this'opening or recess and will effectively stop the rotation of the worm wheel I55 and thus of the driving eccentric 50, and prevent further movement of the knife. The collision of the pin 30I with the rod 215 and the consequent stoppage of the operating parts of the machine beyond the driving head I15 carried by theshaft, I00 will cause the break pins I83 to shear off and the clutch I20 to be disengaged and the brake shoes I68 applied through the mechanism which has already been described.

Normally, of course, the cam .262 operating through the roller 26I on the lever 254 will remove the latch 250 and permit the clutch to disengage and the brake to be applied at the end of each stroke and the mechanism which has just been described is intended to function as a safety mechanism whereby, in the event of failure of the normal operating means, only one stroke of the cutting knife for each deliberate depression of the starting lever can be made. In the absence of such mechanism a second knife stroke might occur through failure of the clutch plates to separate, a deliberate holding down of the starting lever 226, or a breakage ofany of the elements in the train of mechanism intended to effect the stoppage of the machine at the end of one stroke. The latch member 306becomes disengaged from the shoulder 211 of the safety rod 215 through contact of the tail 308 thereof with the inclined surface 309 of the casing I52, upon depression of the safety rod through the counterclockwise swinging of the arm 212 at the end of the cycle of movement of the cutter.

In order to permit the operator to employ the power driven mechanism of the cutter to cause the knife to descend to the bottom of its stroke and rest upon the wooden cutting stick I1 for removing the knife blade or for any other purpose, the following mechanism is provided. Ordinarily, if another complete cutting cycle is intended, the starting lever is swung all the way down and the latch 250 applied, but in this operation, the

operator can jog or inch the clutch to cause the knife to descend slowly or by degrees. During this movement the pin 30I may be brought into contact with the rod 215, but under these circumstances a collision which would cause the break pins to shear will be prevented. To effect this purpose a shield member 3I0 is provided which is secured to the end of the arm 3 of the flat substantially annular member 3I2 which surrounds tne hub 3M of the worm wheel I56. The member 3 I 2 is urged against the face of the wheel I56 by means of the coil spring 3I5 (Figure 15). A spring 3I1 is secured at one end to the shield member 3I0 as at 3I8 and the opposite end of the spring is secured to the pin 30I. This serves to maintain these elements in their relative positions illustrated in Figures and 18 of the drawings. During the inching of the clutch and slow movement of the knife the front edge 320 of the shield 3I0 contacts with the rod 215, the spring 3I'I' will be stretched, and the shield will be held stationary while the pin 30I moves forward into gentle contact with the rod 215. This position is indicated clearly in Figure 20 of the drawings. Now, upon re-engagement of the clutch during this slow inching or jogging of the cutter, the lever 212 will pull the rod 215 outwardly and the spring 3I1 will cause the shield 312 to snap intothe recess 300 in the pin 215 and forwardly against the pin 30I again, as in Figure 1'1 If now, while the shield 3I0 is still passing through the recess 300, the clutch is The clamping mechanism For a clear "disclosure of the mechanism for clamping the pile of paper which is to be cut, reference is made more particularly to Figures 8, 9, and21-26of the'drawings. The paper clamp member is indicated by the reference numeral 358 and is provided with vertical plates or fingers *35l with which the fingers 55' of the back gauge are adaptedto intermesh so that the back gauge 55 can be brought forwardly in order that piles of paper of very narrow width may be cut. The clamp is disposed immediately to the rear of the knife l8 and reciprocates vertically in guides 353 at the sides of the cutter and frame In. The knife blade" is positioned about a half inch above the lower edge ofthe clamp 358 so that the clamp will be able to compress and apply pressure to a pile of paper of the maximum height before the knife contacts the pile.

On each side of the clamp 358 a flat vertically disposed pull bar is secured, from each of which a swivel 352 is suspended. These swivels are connected by means of the short links 353 to the bifurcated arms 355 and 356 of the clamp actuating cranks 351 and 358 which are pivotally .supportedat opposite sides of the machine upon the shafts 368 and -36| respectively, both of these shafts being fixed in the frame I8. The ends of the arms 355 and 356 of the crank levers are connected by means of the flat connecting bar 383which is bent as shown to avoid the hub of the crank member 351. Other short bifurcatedlever arms364 and 365 are formed on the cranks 351 and 358 and are joined by means of the connecting bar 386 which may be lengthened or shortened by means of the turnbuckle 381 provided with the lock nuts 388. This adjustment .is for the purpose of maintaining the paper clamp downwardly from the crank 351.

358 parallel with the table I6.

Upon the longitudinal drive shaft 5|, between the eccentric 58 and the intermediate bearing 52a there is keyed the gear 318. Upon each side of the gear 318 a rocking arm 312 is rotatably mounted on the shaft 5|. The upper ends of each ofthese rocking levers are provided with pins 313 upon which are rotatably-carried the spaced gears 315 both of which mesh with the gear 318, which is of considerable width. A wrist pin 311 is received within the=bushings 318 provided in each of the gears 315 and extends across the space intervening between these gears. A fiat connecting rod 388 provides an operative connection between the wrist pm 311 and the end of the bifurcated lever arm 382 which extends The connecting rod 388 is slotted as at 383 for the reception of the pin 3.84which is secured within the forked ends of the lever 382. A bushing 385 surrounds the pin 384 and fits within the slot 383.

A. rod 388 extends horizontally across the lower portion of the frame l8 from side to side thereof. On the left hand side of the frame as viewed in Figures 21, 25 and 26 the rod '388 passes through a hearing or boss389 and at theright hand side of the frame therod passes through an enlarged opening 398 and thence through the plate 39| which is secured to the'frame l8. Nuts 392 serve to retain the rod in place. A cross head 395 is free to slide upon the rod 388 near the left hand endzthereof and is provided upon each side with the trunnion pins 396 to which the ends of the with slots 399 through which the studs 488 are passed. These studs also pass through openings in the pull bars 391 and serve to adjustably connect these bars with the rocking arms 312 by selectively positioning the studs within the slots 399, for a purpose to be disclosed as the description proceeds. The nuts 85H serve to clamp the studs 488 to the arms 312. An elongated coil spring 485 surrounds the rod 388 and is confined under partial compression between the cross head 395 and the plate 39L A series of sleeves 485 is placed under the coils of the spring 485 and is free to slide over the rod 388. At intervals, tongues 481 formed on the sleeves 486 project between the coils of the springs 485. The function of these sleeves is to reduce wear on the rod .388 which would be considerable if the coils. of the spring 485 were in direct contact with the rod 388.

One of the bifurcations of the arm 365 of the right hand clamp operating crank 358 is provided with an extension 488 on which the swivel 489 pivots. The spring guide rod 4|8 is fastened in the swivel 489 and projects through an opening in the boss 4|| formed on the left hand side of the main frame l8. A pre-loaded coil spring M2 is guided on the rod 4! and is compressed between the boss 4H and the shouldered swivel 489, for the purpose of maintaining the clamp 358 in raised position.

The operation of the automatic clamp mechanism is as follows. Upon engagement of the clutch I28 the shaft 5| will begin its rotation, its cycle of movement as already described comprising a single rotation in order, through the driving eccentric 58, to cause the knife l8 to descend through the material to be cut and then return to its uppermost position. During this cycle the shaft 5| will rotate the gear 318 in a clockwise direction as indicated by the arrows in Figures 21, and 26. The gears 315 which mesh with the gear 318 will rotate in a counterclockwise direction as indicated, and the wrist pin 311 will pass from its left hand dead center position shown in Figure 21 downwardly to the position indicated in Figure 25, at which point the clamp 358 will have been brought into firm contact with the pile of paper A. At this point the rotation of the clamp cranks 351 and 358 practically ceases. The pin 384 to which an end of the connecting bar 388 is connected also becomes substantially stationary. Then the continued rotation of the gears 315 through the driving action of the gear 318 will cause these gears 315 to make a planetary movement around the shaft 5| as a center, rocking the arms 312 in a counterclockwise direction until the wrist pin 311 passes through the right hand dead center position shown in Figure 26 of the drawings. This movement of the arms 312, through the pull bar connections 391 and the cross head 395, compresses the spring 485, and the pressure of this spring is amplified through the ratio of the gears and levers forming the operative connections of the clamping mechanism and transmitted to the pile of paper A during the cutting stroke of the knife. The required clamping pressure to prevent the bevel of the cutting blade 28 from shifting the sheets A from the back gauge 55 is quite considerable, amounting to several tons in the average cutter of this type.

It will be clearly apparent from the foregoing description that the higher the pile of paper A, the sooner the wrist pin 311 comes to its substantially stationary position and the greater the suball chine.

sequent planetary movement of the gears 315. This results in a greater degree of compression in the spring 405 and consequently a greater developed pressure on the paper clamp 350. Thus, the amount of pressure on the pile of paper automatically adjusts itself to the height of the pile.

Another feature of this novel arrangement is that when the machine is at rest, the pre-compression. pressure of the spring 405 is absorbed by the rod 388 in tensile stress on the nuts 302 and in compression on the hub or bearing 350 of the frame I0. Thus an additional safety feature is provided in that the spring 405 does not exert a torque on the driving mechanism which would be a source of danger to the operator of the ma- Furthermore, since the spring 405 is not compressed to the maximum amount when the machine is at rest, the life of the spring is met-- terially increased. The amount of clamping pressure to be applied may be reduced by loosening the nuts 40I on the studs 400, moving the pull bar assembly 307, 398 upwardly and tightening the nuts 4IJI again after the studs have assumed their new positions at a higher point within the slots 399. This decrease in pressure will result from a somewhat decreased leverage as well as from a reduction in spring compression.

For the purpose of bringing the paper clamp 350 down upon the pile of paper A temporarily as, for example, in order to indicate to the operator the point at which the knife will cut the paper or in order to hold curly or easily disturbed paper stock before the full automatic clamping pressure is applied, there is provided a .treadle operated means for actuating the clamp.

For the clearest disclosure of this mechanism, reference is made to Figures 8 and 21. The treadle 420 extends longitudinally of the frame at the lowermost portion thereof and passes through slots 42I and 422 formed respectively in the front and rear walls II and I2. The rear end of the treadle is provided with a sleeve 424 which surrounds the drive shaft section I50 which provides a fulcrum for the treadle. An

arm 425 extending upwardly from the treadle is pivotally connected as at 426 with the lower end of the link 42'! which is provided with a slot 428 which receives the pin 420 carried by the connecting bar 363 which extends between the clamp operating arms 355 and 356 of the cranks 35! and 358. The slot 428 provides a lost motion connection which will prevent the movement of the treadle when the clamp is operated by the automatic drive. The hub or sleeve 424 of the treadle is also provided with an upwardly extending forked arm 450 to the upper end of which is pivotally connected one end of the spring rod 432. A spring stop 434 is secured to this rod and serves to compress the spring 435 against the boss 435 carried by the front wall I I of the frame and into which the end of the rod 432 is guided. The spring 435 counterbalances the weight of the treadle 420 and maintains it, when in idle position, against the end 437 of the slot MI in. the front wall I I of the frame. When the treadle 420 is depressed, the connecting bar 363 is pulled downwardly by means of the link 421 thus rotating the cranks 351 and 350 and depressing the clamp 350. During this manual movement the pin 384 carried by the lever arm 382 of the crank 35? moves idly in the slot 383 formed in the driving connecting rod 380. When the foot pressure is released, the pressure of the spring 4H] will raise the clamp 350 through its connection with the clamp crank 358.

Operation The operation of the cutting machine will now be reviewed or summarized and there will be pointed out in connection therewith the functioning of the various safety devices under abnormal or emergency conditions. The paper to be cut is placed upon the table I6 against the back gauges 55 which have already been locked in position determined by the width of the sheet desired which is indicated on the graduated tape 85 as viewed through the opening 86. The point at which the knife will strike the paper may be determined by depressing the clamp 350 by means of the treadle 420. This will give the position of contact of the knife edge rather accurately since the forward edge of the clamp 350 is disposed just adjacent the edge of the knife blade as clearly indicated in Figure 8 of the drawings. If the paper is thin or has a tendency to curl, the clamp 350 may be held in depressed position by the foot treadle until the automatic clamping mechanism comes into play during the cutting stroke.

The paper having been placed in proper position upon the table I6, the hand lever 226 is depressed, thus moving the levers 22L 205 and 200 in directions which will cause the plates of the clutch I20 to engage and the rod 235 to be moved through the eye of the bolt 236 permitting the latch 250 to move into position between the head 238 of the rod 235 and the eye bolt 236 as shown in Figures 11 and 12. This movement will also disengage the brake shoes I68 and I69 from the brake wheel I65 and start the rotation of the driving eccentric 50 carried by the shaft 5i. The depression of the hand lever 226 will, through the rotation of the shaft 225 and the hub or sleeve 220, rock the bifurcated lever arm 212 in a clockwise direction and raise the safety bar 2'l5 so that the pin I .on the worm wheel I56 may pass through the notch 300 in the bar 2l5, as shown in Figure 16. Continued rotation of the shaft-5i and eccentric 50 will cause the knife- I8 to descend, cut the paper, and return to its uppermost position. At the end of this cycle of movement, the cam 262 will rock the lever 254, throw the latch 250 out of its position beneath the head 238 of the rod 235 and the spring 240 will force the rod downwardly and reverse the movement of the levers 205 and 206, thus releasing the clutch I20 and setting the brake I65, I60. Through the link 222 connecting the levers 222i and 223, the starting shaft 225 and its lever 242 will be rotated in a counterclockwise direction, and will cause the rod 215 to descend and release the latch 306, as indicated in the upper portion of Figure 20. During this cycle of operation, the automatic clamp 350 is operated as already described.

In case an overload on the cutter is encountered during the operation of the device, the break pins I63 which provide the driving connection between the members I65 and H5 carried respectively by the shaft sections I50 and I00 will be sheared off and the cam headed pins295 will force the driving member I15 away from the member 555, this resulting, through the contact of the member I l5 with the roller 290, in rotating the crank 280 and, through the link 285 and the lever arm 245, releasing the latch 250 and permitting the spring 240 to throw out the clutch I20 and apply the brake shoes I68, thus stopping the cutting operation immediately.

Even though the starting hand lever 226 is held down after a single out has been completed, either purposely or through some inadvertence, the cutter will not pass through more than one cycle of operation. Repeating of the cutting movement is prevented by the following operations. The wedge 305 carried by the worm Wheel I56 will draw the safety rod 215 inwardly as shown in Figure 18 of the drawings whereupon the latch 306 will catch on the shoulder 21'! of the rod 275 as shown in Figure 19, and retain the rod in its inward position regardless of the position of the lever 212 connected with the hand crank 226. Then after completion of one rotation of the worm wheel I56, the pin 30| will strike the rod 215 and further rotation will be prevented. This collision would, of course, cause the break pins I83 to shear and the clutch would be disengaged and brake shoes [68 would be applied.

A similar operation would ensue through failure of the clutch plates to release at the end of the first revolution.

The operation of the device may be halted at any point during its cycle of movement by a reverse rotation of the starting lever 226. This will cause the lever arm 2H to descend, contact with the sleeve 25'! connecting the ends of the levers 246 and 255 and depress this connection, thus releasing the latch 250 and disengaging the clutch I20 and applying the brake.

It is to be understood that the embodiment of the invention shown and described herein is for illustrative purposes only and that various changes and modifications may be made therein without departing from the scope of the invention as defined in the following claims.

Having thus described the invention, what is claimed as new and desired to be secured by Letters Patent is:

1. In a cutting machine of the class described, in combination, a work support, means for clamping the work on said support, a knife, means for operating said knife and said clamping means, transmission mechanism connecting said operating means with said knife and said clamping means, and a break pin incorporated in said transmission and adapted to be severed upon the occurrence of an overload or obstruction to the operation of said transmission means beyond a predetermined amount.

2. In a cutting machine of the class described, in combination, a work support, a knife, means for operating said knife, transmission mechanism connecting said operating means with said knife, said transmission mechanism including a pair of aligned rotatable shafts, driving and driven members respectively carried by the adjacent ends of said shafts, a break pin connecting said members at points radially outward from their centers, and adapted to be severed upon the occurrence of overload, means for moving one of said members longitudinally of its shaft upon the breaking of the pin, and means actuated by said movement to stop said transmission.

3. In a cutting machine of the class described, in combination, a work support, a knife, means for operating said knife, transmission mechanism connecting said operating means with said knife, said transmission mechanism including a pair of aligned shafts, driving and driven members carried by the adjacent ends of said shafts, a break pin connecting said members at points radially outward from their centers, and adapted to be severed upon the occurrence of overload, chucks disposedin adjacent faces of said members at points spaced radially from their centers and adapted to receive the opposite end of a break pin which is adapted to shear upon the occurrence of unusual resistance to operation of the device, at least one of said chucks being removable for replacing the break pin.

4. In a cutting machine of the class described, in combination, a work support, a knife, power means for operating said knife, transmission means connecting said knife and said power means, a frangible connection in said transmission means adapted to break in the event an overload on said cutter or an obstruction to the operation of the transmission is encountered, and means automatically operable upon the breaking of the frangible connection adapted to disconnect said transmission mechanism for said power means.

5. In a cutting machine of the class described, in combination, a work support, a knife, power means for operating said knife, transmission mechanism operatively connecting said knife with said power means, a frangible connection embodied in said transmission means adapted to break in the event of an overload on said cutter or an obstruction to the operation of said transmission means is encountered, a clutch disposed in said transmission means on the power side of said frangible connection, and a brake disposed upon the knife side of said connection and adapted to be applied to an element of said transmission to stop the knife, and means operable upon the breaking of said frangible connection to release said clutch and apply said brake.

6. In a cutting machine of the class described, in combination, a work support, a knife, power means for operating said knife, transmission mechanism operatively connecting said knife with said power means, a frangible connection embodied in said transmission means adapted to break in the event of an overload on said cutter or an obstruction to the operation of said transission means is encountered, a clutch disposed in said transmission means and a brake adapted to be applied to an element of said transmission to stop the knife, and means operable upon the breaking of said frangible connection to release said clutch and apply said brake.

7. In a cutting machine of the class described, in combination, a work support, a knife, power means for operating said knife, transmission mechanism operatively connecting said knife with said power means, said transmission mechanism including two adjacent rotatable shafts, driving and driven members respectively carried by the adjacent ends of said shafts, said driven member constituting a brake wheel, a brake element adapted to be applied to said wheel, a break pin driving connection between said members which is adapted to be severed upon the occurrence of overload, and means for automatically applying said brake upon the severing of the driving connection between said members.

8. In a cutting machine of the class described, in combination, a work support, a knife, power means for operating said knife, transmission mechanism operatively connecting said knife with said power means, said transmission mechanism including a driving member and a driven member, said driven member constituting a brake wheel, a brake element adapted to be applied to said wheel, a frangible driving connection between .said members which is adapted to be broken upon the occurrence of overload, a clutch interposed in said transmission mechanism between said power means and said driving member, and means for automatically releasing said clutch and applying said brake upon the breaking of said driving connection between said members.

9. In a cutting machine of the class described, in combination, a work support, a knife, power means for operating said knife, transmission mechanism operatively connecting said knife with said power means, said transmission mechanism including a driving member and a driven member, said driven member constituting a brake wheel, a brake element adapted to be applied to said wheel, a break pin driving connection between said members which is adapted to be severed upon the occurrence of overload, a clutch interposed in said transmission mechanism between said power means and said driving member, and means for moving said driving and driven members apart upon the severing of said driving connection, and means actuated by said movement for applying said brake and releasing said clutch.

10. In a cutting machine of the class described, in combination, a work support, a knife, power means for operating said knife, transmission mechanism operatively connecting said knife with said power means, said transmission mechanism including a driving member and a driven member, a clutch interposed in said transmission mechanism between said power means and said driven member, a break pin driving connection between. said members which is adapted to be broken upon the occurrence of overload, wedging means on one of said members adapted to move said members apart upon the occurrence of relative movement between the two, operative connections between one of said members and said clutch, whereby upon relative movement between said members said clutch is released.

11. In a cutting-machine of the class described, in combination, a work support, a knife, power means for operating said knife, transmission mechanism operatively connecting said knife with said power means, a frangible connection embodied in said transmission mechanism, a stop element adapted to be positively interposed in said transmission on the knife side of said frangible connection, non-repeat mechanism for interposing said stop element during the cycle of operation of the knife, whereby upon continued operation of said power and transmission means beyond the completion of one cycle of operation of l the knife, said frangible connection will break.

12. In a cutting machine of the class described, in combination, a work support, a knife, power means for operating said knife, transmission mechanism operatively connecting said knife with said power means, a frangible connection embodied in said transmission mechanism, nonrepeat mechanism adapted to stop the movement of said knife substantially at the end of one cycle of movement thereof, whereby said frangible connection will break if said power means and said transmission mechanism are operated beyond the completion of said cycle of movement.

13. In a cutting machine of the class described, in combination, a work support, a knife, power means for operating said knife, transmission mechanism operatively connecting said knife with said power means, a frangible connection embodied in said transmission mechanism, a stop element adapted to be positively interposed in said transmission on the knife side of said frangible connection, nonrepeat mechanism for interposing said stop element during the cycle of operation of the knife, whereby upon continued operation of said power and transmission means beyond the completion of one cycle of operation of the knife, said frangible connection will break, a clutch interposed in said transmission between said power means and said frangible connection, a brake adapted to be applied to an element of said transmission between said frangible connec tion and said knife, means set in operation by the breaking of said frangible connection to release said clutch and apply said brake.

14. In a cutting machine of the class described, in combination, a work support, a knife, power means for operating said knife, transmission mechanism operatively connecting said knife with said power means, said transmission including two aligned shafts, driving and driven members respectively carried by the adjacent ends of said shafts, a frangible driving connection between said members adapted to be broken upon the occurrence of overload, a cam headed pin carried by one of said members, and adapted to normally fit into a similarly cam shaped recess in the other of said members, one of said members being shiftable longitudinally on its shaft, a clutch interposed between said power means and said transmission operatively connecting between said shiftable member and said clutch whereby upon breaking of said frangible connection continuous rotation of one of said members with respect to the other will cause the cams to shift said member and release the clutch.

15. In a device of the class described, in combination, a releasable driving connection comprising aligned driving and driven shafts, driving and driven heads respectively carried by the adjacent ends of said shafts, one of said heads being 1ongitudinally movably mounted on its shaft, a break pin socketed in each of said heads at points radially spaced from the axis of said shafts and adapted to break upon theoccurrence of overload on the driven shaft, a boss having an inclined face on one of said heads and adapted normally to be received within a recess in the other of said heads having a similarly inclined face, said coop-' erating boss and recess also being spaced from the axis of said shaft, whereby upon relative rotation of said shafts upon severing of the break pin, said longitudinally movable head will be shifted away from the other of said heads.

16. In a cutting machine of the class described, in combination, a work support, a knife, power means for operating said knife, transmission mechanism operatively connecting said knife with said power means, said transmission mechanism including a clutch for connecting and disconnecting said mechanism from said power means, means continually urging the members of said clutch toward disengagement, manually operable means for engaging said clutch in opposition to said last named means, a detent member adapted to be applied to said urging means by operation of said manually operable means to prevent disengagement, and means set in motion by the occurrence of an overload on said cutter to release said detent.

17. In a cutting machine of the class described, in combination, a work support, a knife, power means for operating said knife, transmission mechanism operatively connecting said knife with said power means, said transmission mechanism including a clutch for connecting and disconnecting said mechanism from said power means, resilient means continually urging the members of said clutch toward disengagement, manually 1 operable means for engaging said clutch in opposition to said resilient means, a detent member adapted to be applied to said resilient means by operation of said manually operable means to prevent disengagement, and manually operable means for releasing said detent.

18. In a cutting machine of the class described, in combination, a work support, a knife, power means for operating said knife, transmission mechanism operatively connecting said knife with said power means, said transmission mechanism including a clutch for connecting and disconnecting said mechanism from said power means, spring pressed means continually urging the members of said clutch toward disengagement, manually operable means for engaging said clutch in opposition to said spring pressed means, a detent member adapted to be applied to said spring pressed means by operation of said manually operable means to prevent disengagement, and means automatically operative substantially at the end of one cycle of movement of said knife to release said detent.

19. In a cutting machine of the class described, in combination, a work support, a knife, power means for operating said knife, transmission mechanism operatively connecting said knife with said power means, said transmission mechanism including a clutch for connecting and disconnecting said mechanism from said power means, spring pressed means continually urging the members of said clutch toward disengagement, manually operable means for engaging said clutch in opposition to said spring pressed means, a detent member adapted to be applied to said spring pressed means by operation of said manually operable means to prevent disengagement, said transmission connection also including a frangible connection adapted to break upon the encountering of excessive resistance to operation of the cutter, and means set in motion by the breaking of said connection to release said detent and thus effect the disengagement of the clutch.

20. In a cutting machine of the class described, in combination, a work support, a knife, power means for operating said knife, transmission mechanism operatively connecting said knife with said power means, said transmission mechanism including a clutch for connecting and disconnecting said mechanism from said power means, spring pressed means continually urging the members of said clutch toward disengagement, manually operable means for engaging said clutch in opposition to said spring pressed means, a detent member adapted to be applied to said spring pressed means by operation of said manually operable means to prevent disengagement, said transmission connection also including a frangible connection adapted to break upon the encountering of excessive resistance to operationof the cutter, means set in motion by the breaking of said connection to release said detent and thus effect the disengagement of the clutch,

, and a non-repeat device adapted to release said detent and disengage said clutch at the end of one cycle of movement of said cutter.

21. In a cutting machine of the class described, in combination, a work support, a knife, power means for operating said knife, transmission mechanism operatively connecting said knife with said power means, said transmission mechanism including a clutch for connecting and disconnecting said mechanism from said power means, spring pressed means continually urging the members of said clutch toward disengagement, manually operable means for engaging said clutch in opposition to said spring pressed means, a detent member adapted to be applied to said spring pressed means by operation of said manually operable means to prevent disengagement, said transmission connection also including a frangible connection adapted to break upon the encountering of excessive resistance to operation of the cutter, means set in motion by the breaking of said connection to release said detent and thus effect the disengagement of the clutch, a positive stop means for said cutter, non-repeat mechanism adapted to be automatically actuated during one cycle of movement of the cutter to set said positive stop means to halt the operation of the knife substantially at the end of one cycle of movement whereby said frangible connection is broken and said clutch is disengaged.

22. In a cutting machine of the class described, in combination, a work support, a knife, power means for operating said knife, transmission mechanism operatively connecting said knife with said power means, said transmission mechanism including a clutch for connecting and disconnecting said mechanism from said power means, spring pressed means continually urging the members of said clutch toward disengagement, manually operable means for engaging said clutch in opposition to said spring pressed means, a detent member adapted to be applied to said spring pressed means by the operation of said manually operable means to prevent disengagement, said transmission connection also including a frangible connection adapted to break upon the encountering of excessive resistance to operation of the cutter, means set in motion by the breaking of said connection to release said detent and thus effect the disengagement of the clutch, a non-repeat device adapted to release said detent and disengage said clutch at the end of one cycle of movement of said cutter, a positive stop means for said cutter, another nonrepeat mechanism adapted to be automatically actuated during one cycle of movement of the cutter to set said positive stop means to halt the operation of the knife substantially at the end of one cycle of movement whereby said frangible connection is broken and said clutch is disengaged, in case of failure of said first mentioned non-repeat mechanism.

23. In a cutter of the class described, in combination, a work table, a knife, power means for operating said knife, transmission means operatively connecting said knife with said power means, a stop member movable into and out of the path of an element of said transmission, starting means for said transmission mechanism and knife, means operatively connected with said starting means for withdrawing said stop member from the path of said element to permit the passing of said element, means for automatically returning said stop to its effective position in the path of said element after it has once passed said stop member to prevent a second cut of said knife without a positive release of said stop means.

24. In a cutter of the class described, in combination, a work table, a knife, power means for operating said knife, transmission means operatively connecting said knife with said power means, a rotary member embodied in said transmission, a rigid projection on said rotary member, a stop member movable into and out of the orbit of said projection, starting means for said transmission mechanism and knife, means operatively 

